7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 1/25
Project : NOEV Lube Oil Blending Plant
Job Number : AL-2524
Document Number : V-2151-102-A-216
Reference Drawing : V-2151-102-A-201_Rev.C & V-2151-102-A-215_Rev.B
Package Name : Filter
Tag Number : F-901A/B, F-902A/B, F-903A/B, F-904A/B, F-905A/B, F-906A/B
C 27-May-2013
B 20-May-2013
A 27-Mar-2013
Rev Date
L.A.V
Checked
L.N.B
L.N.B
L.N.B
DESIGN CALCULATION SHEET
Description Prepared Approval
Issue for review / approval
Issue for review / approval
Issue for review / approval L.D.T
L.D.T
L.D.T
L.A.V
L.A.V
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 2/25
Project: NOEV Lube Oil Blending Plant Job No.: AL-2524 Rev. No
INDEX PAGE
1. Design Data 2
2. Shell Thickness Calculation 2
3. Bottom Head Thickness Calculation 3
4. Top Head Thickness & Swing Bolt Diameter Calculation 3
5. Nozzle Calculation 4
6. Weld Size Calculation 7
7. Reinforcement 8
8. Weight Calculation Sheet 109. Wind load Analysis 10
10. Seismic Analysis 11
11. Skirt Support design for Wind/Seismic 12
12. Lifting Lug Calculation 17
13. Hydrotest Pressure 20
14. Conclusion 21
DESIGN CALCULATION SHEET
Page 1 of
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 3/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
1. Design Data
Design Code : ASME Sec VIII Div.1 2010 Ed., 2011a add.
Code Stamp: No
Service: Lube Oil
Design pressure
Internal pressure P = 11.8 bar = 1.18 MPa
External pressure 0.0 bar = 0.0 MPa
Working pressure 4.8 bar = 0.48 MPa
Design temperature 105.0 degree C
Working temperature 40 degree C
Corrosion allowance 0.0 mm
Vessel inside diameter 396 mm (O/D = 406 mm)
Vessel length (T to T) 1020 mm
Bottom Head type: 2:1 Ellipsoidal Head
MinimumDesignMetalTemperature 6.0 degree C
Material
Shell SA-240M TP304/304L
Head SA-240M TP304/304L
Nozzle Flange SA-182M F304/304L or SA-240M TP304/304L
Nozzle Neck (Pipe) SA-312M TP304/304L
Skirt Support SA-240M TP304/304L
Nozzle Flange: ASME B16.5 Standard
SCH THK.
N1 150 40S 5.49
N2 150 40S 5.49
N3 150 80S 3.91
N4 150 80S 3.91
HH 150 - 5
2. Shell Thickness Calculation (Refer to UG-27)
2.1 Minimum required thickness of shell exclusive corrosion allowance (t):
Circumferential Stress (Longitudinal Joints)
1.18 x 198.0
115.0 x 0.85 - 0.6 x 1.18
where:
P : internal design pressure P = 1.18 MPa < 0.385SE = 37.634 MPa
R : Inside radius of the shell R = 198.0 mm
S : Maximum allowable stress value S = 115.0 MPa
E : Joint efficiency E = 0.85
Longitudinal Stress (Circumferential Joints)
1.18 x 198.0 233.6
2.0 x 115.0 x 0.85 + 0.4 x 1.18 196.0
where:
DN 80 (3") SO RF 88.9 77.92
DN 20 (3/4") SO RF 26.7 18.88
DN 20 (3/4") SO RF 26.7 18.88
DN 400 (16") SO RF 406 396
==
= =
97.0
Nozzle Size Flange Type ClassNozzle Neck Nozzle outside
diameter, mm
Nozzle inside
diameter, mm
DN 80 (3") SO RF 88.9 77.92
mm
mm
2.41
= 1.19
=233.6
Page 2 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 4/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
E : Joint efficiency E = 0.85
Degree of Radiographic Examination: Spot
2.2 Minimum Thickness of Pressure retaining Components (UG-16 (b)) = 2.5 mm
2.3 Choose Nominal thickness of shell, ts = 5 mm
3. Bottom Head Thickness Calculation (Refer to UG-32)
Type of head: 2:1 Ellipsoidal Head
3.1 Minimum required thickness of Head exclusive corrosion allowance (t):
1.18 x 396.0 467.3
2.0 x 115.0 x 1.00 - 0.2 x 1.18 229.8
where:
P : internal design pressure P = 1.18 MPa < 0.385SE = 44.275 MPa
D : Inside diameter of the head skirt D = 396.0 mm
S : Maximum allowable stress value S = 115.0 MPa
E : Joint efficiency E = 1.00
3.2 Minimum required thickness of Head included corrosion allowance
= 2.03 + 0.0 = 2.03 mm
3.3 Minimum required thickness of Head, ts = Min. 2.03 mm
3.4 MDMT
Refer to UG-20 (f): MDMT = -29 degree C
4. Top Head Calculation (Refer to ASME B16.5)
4.1 Thickness of Top Head
Thickness of Top Head selected base on thickness of Blind Flange DN400 (16") ASME B16.5 Pressure Rating 150
Material: SA-240 TP304/304L (Material Group 2.3)
=> Top Head thickness = 37 mm (included raise face)
4.2 Swing Bolt diameter
Bolt material SA-193 GR.B8
Allowable stress of bolt material = 112.8 MPa (refer to ASME Section II, Part D)
Compress force on Top Head, F = A x P = N
Tensile force per one bolt, f = F / n = 9083 N
Tensile strenght per one bolt, τ = f / Ab = 45.18 MPa < 112.8 MPa
Result : PASS
where
A = 123163 mm2 area of Top head resist internal pressure
P = 1.18 MPa internal design pressure
n = 16 quantity of bolt
145332.3
= = mm2.03=
Page 3 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 5/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
db = 16 mm diameter of bolt
Ab = 201.1 mm^2 section area of bolt
5. Nozzle calculation (Refer to UG-45)
5.1 Nozzle Neck N1, N2_DN 80 (3")
Minimum Nozzle neck thickness
where:
S : Maximum allowable stress value S = 115.0 MPa
E : Joint efficiency E = 1.00
Nozzle inside radius Rn = 38.96 mm
tn (min) : minimum required thickness of Nozzle
5.1.1 ta : minimum neck thickness required for internal and external pressure using UG-27 and UG-28
(plus corrosion allowance), as applicable. The effects of external forces and moments from supplemental
loads (see UG-22) shall be considered. Shear stresses caused by UG-22 loadings shall not exceed 70%
of the allowable tensile stress for the nozzle material.
1.18 x 38.96 45.973
115.0 x 1.00 - 0.6 x 1.18 114.3
ta = 0.40 + 0.0 = 0.40 mm
5.1.2 = min ( 4.80 , 2.50 ) = 2.50 mm
where:
tb1 : for vessels under internal pressure, the thickness (plus corrosion allowance) required for pressure
(assuming E = 1.0) for the shell or head at the location where the nozzle neck or other connection
attaches to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b).
tb1 = 2.50 mm
tb2 : for vessels under external pressure (not applicable to this vessel)tb2 = 0 mm
Max (tb1, tb2) = Max ( 2.50 , 0.0 ) = 2.50 mm
tb3 : the thickness given in Table UG-45 plus the thickness added for corrosion allowance.
(for standard wall pipe)
tb3 = 4.8 + 0.0 = 4.80 mm
=> = max ( 0.40 , 2.50 ) = 2.50 mm
5.1.3 Choose Nozzle Neck thickness = 5.49 mm (SCH 40S)
5.1.4 Nozzle actual thickness is compared with the minimum thickness provided which for pipe
material would include a 12.5% undertolerance
= 0.875 x 5.49 = 4.80 > tn (min) = 2.50 mm
Result: the actual thickness provided meets the rules of UG-45 <PASS>
5.2 Nozzle Neck N3_DN 20 (3/4")
Minimum Nozzle neck thickness
= = = 0.40 mm
bant t t ,max(min)
bant t t ,max(min)
bant t t ,max(min)
Page 4 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 6/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
where:
S : Maximum allowable stress value S = 115.0 MPa
E : Joint efficiency E = 1.00
Nozzle inside radius Rn = 9.44 mm
tn (min) : minimum required thickness of Nozzle
5.2.1 ta : minimum neck thickness required for internal and external pressure using UG-27 and UG-28
(plus corrosion allowance), as applicable. The effects of external forces and moments from supplemental
loads (see UG-22) shall be considered. Shear stresses caused by UG-22 loadings shall not exceed 70%
of the allowable tensile stress for the nozzle material.
1.18 x 9.44 11.139
115.0 x 1.00 - 0.6 x 1.18 114.3
ta = 0.10 + 0.0 = 0.10 mm
5.2.2 = min ( 2.51 , 2.50 ) = 2.50 mm
where:
tb1 : for vessels under internal pressure, the thickness (plus corrosion allowance) required for pressure
(assuming E = 1.0) for the shell or head at the location where the nozzle neck or other connection
attaches to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b).
tb1 = 2.50 mm
tb2 : for vessels under external pressure (not applicable to this vessel)
tb2 = 0 mm
Max (tb1, tb2) = Max ( 2.50 , 0.0 ) = 2.50 mm
tb3 : the thickness given in Table UG-45 plus the thickness added for corrosion allowance.
(for standard wall pipe)
tb3 = 2.51 + 0.0 = 2.51 mm
=> = max ( 0.10 , 2.50 ) = 2.50 mm
5.2.3 Choose Nozzle Neck thickness = 3.91 mm (SCH 80S)
5.2.4 Nozzle actual thickness is compared with the minimum thickness provided which for pipe
material would include a 12.5% undertolerance
= 0.875 x 3.91 = 3.42 > tn (min) = 2.50 mm
Result: the actual thickness provided meets the rules of UG-45 <PASS>
5.3 Nozzle Neck N4_DN 20 (3/4")
Minimum Nozzle neck thickness
where:
S : Maximum allowable stress value S = 115.0 MPa
E : Joint efficiency E = 1.00
Nozzle inside radius Rn = 9.44 mm
tn (min) : minimum required thickness of Nozzle
5.3.1 ta : minimum neck thickness required for internal and external pressure using UG-27 and UG-28
(plus corrosion allowance), as applicable. The effects of external forces and moments from supplemental
= 0.10 mm= =
bant t t ,max(min)
bant t t ,max(min)
Page 5 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 7/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
loads (see UG-22) shall be considered. Shear stresses caused by UG-22 loadings shall not exceed 70%
of the allowable tensile stress for the nozzle material.
1.18 x 9.4 11.139
115.0 x 1.00 - 0.6 x 1.18 114.3
ta = 0.10 + 0.0 = 0.10 mm
5.3.2 = min ( 2.51 , 37.0 ) = 2.51 mm
where:
tb1 : for vessels under internal pressure, the thickness (plus corrosion allowance) required for pressure
(assuming E = 1.0) for the shell or head at the location where the nozzle neck or other connection
attaches to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b).
tb1 = 37.00 mm
tb2 : for vessels under external pressure (not applicable to this vessel)
tb2 = 0 mm
Max (tb1, tb2) = Max ( 37.00 , 0.0 ) = 37.0 mm
tb3 : the thickness given in Table UG-45 plus the thickness added for corrosion allowance.
(for standard wall pipe)
tb3 = 2.51 + 0.0 = 2.51 mm
=> = max ( 0.10 , 2.51 ) = 2.51 mm
5.3.3 Choose Nozzle Neck thickness = 3.91 mm (SCH 80S)
5.3.4 Nozzle actual thickness is compared with the minimum thickness provided which for pipe
material would include a 12.5% undertolerance
= 0.875 x 3.91 = 3.42 > tn (min) = 2.51 mm
Result: the actual thickness provided meets the rules of UG-45 <PASS>
6. Weld size calculation (Refer to UW-16)
6.1 Nozzle N1 & N2 to Shell weld joints
6.1.1 Size of weld / Shell thickness
tn (actual) = 5.49 mm
Fillet Leg Length = 6.00 mm
=> tc (actual) = 4.20 mm
t = 5.00 mm
6.1.2 Check for full penetration groove weld and fillet cover weld shown in Fig above
tc (min) = Min ( 6 , 0.7 tmin )
where:
tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fil let, single-bevel, or single-J weld
tmin = Min ( 19.0 , 5.49 , 5.00 ) = 5.49 mm
0.7tmin = 0.7 x 5.49 = 3.84 mm
=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 3.84 ) = 3.84 < tc (actual) = 4.2 mm
= 0.10 mm= =
bant t t ,max(min)
Page 6 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 8/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. N
=> PASS
6.2 Nozzle N3 to Bottom Head weld joint
6.2.1 Size of weld / Shell thickness
tn (actual) = 3.91 mm
Fillet Leg Length = 6.00 mm
=> tc (actual) = 4.20 mm
t = 2.03 mm
6.2.2 Check for full penetration groove weld and fillet cover weld shown in Fig above
tc (min) = Min ( 6 , 0.7 tmin )
where:
tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fillet, single-bevel, or single-J weld
tmin = Min ( 19.0 , 3.91 , 2.03 ) = 3.91 mm
0.7tmin = 0.7 x 3.91 = 2.74 mm
=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 2.74 ) = 2.74 < tc (actual) = 4.2 mm
=> PASS
6.3 Nozzle N4 to Top Head weld joint
6.3.1 Size of weld / Shell thickness
tn (actual) = 3.91 mm
Fillet Leg Length = 6.00 mm
=> tc (actual) = 4.20 mm
t = 37.00 mm
6.3.2 Check for full penetration groove weld and fillet cover weld shown in Fig above
tc (min) = Min ( 6 , 0.7 tmin )
where:
tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fillet, single-bevel, or single-J weld
tmin = Min ( 19.0 , 3.91 , 37.00 ) = 3.91 mm
0.7tmin = 0.7 x 3.91 = 2.74 mm
=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 2.74 ) = 2.74 < tc (actual) = 4.2 mm
=> PASS
7. Reinforcement
7.1 Reinforcement for Nozzle N3, N4_DN 20 (3/4")
Refer to UG-36C (3) reinforcements are not required for Nozzle 2" and smaller
7.2 Reinforcement for Nozzle N1, N2_DN 80 (3")
Reinforcement material: SA-240 TP304/304L
Dp : outside diameter of reinforcing element = 150 mm
te : thickness or height of reinforcing element = 5 mm
A : total cross-sectional area of reinforcement required in the plane under consideration
Page 7 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 9/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev.
(includes consideration of nozzle area through shell if Sn /Sv < 1.0)
A = dtr F + 2tn tr F (1-f r1) = 194.8 mm2
A1 : area in excess thickness in the vessel wall available for reinforcement
(includes consideration of nozzle area through shell if Sn /Sv<1.0)
A1 = larger of below value = 195 mm2
d(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 194.8 mm2
2(t + tn)(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 52.45 mm2
A2 : area in excess thickness in the nozzle wall available for reinforcement (see Fig. UG-37.1)
A2 = smaller of below value = 74.5 mm2
5(tn - tr n) f r2t = 74.5 mm2
5(tn - tr n) f r2tn = 81.8 mm2
A3 : area available for reinforcement when the nozzle extends inside the vessel wall
A3 = min (5t ti f r2, 5ti ti f r2, 2h ti f r2) = 0 mm2
A5 : cross-sectional area of material added as reinforcement
A5 = (DP - d - 2tn)te f r4 = 305.5 mm2
where:
d : finished diameter of circular opening or finished dimension = 77.92 mm
h : distance nozzle projects = 0 mm
t : specified vessel wall thickness = 5 mm
tn : nozzle wall thickness = 5.49 mm
tr : required thickness of a seamless shell = 2.5 mm
tr n : required thickness of a seamless Nozzle wall = 2.5 mm
ti : nominal thickness of internal projection of nozzle wall = 0 mm
S : allowable stress value in tension = 115.0 MPa
Sn : allowable stress in nozzle = 115.0 MPa
Sp : allowable stress in reinforcing element = 115.0 MPa
Sv : allowable stress in vessel = 115.0 MPa
Page 8
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 10/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524
F : correction factor = 1
E1 = 1
f r1 = 1
f r2 = Sn /Sv = 1
f r3 = Min (Sn/S or Sp/S) = = 1
f r4 = Sp /Sv = 1
A1 + A2 + A3 + A5 = 575 mm2 > A = 195 mm2
RESULT : PASS
8. Weight Calculation Sheet
No.Thickness
(mm)Q'ty
Unit
Weight
(kg)
Total
Weight
(kg)
1 Shell 5.0 1 54.2 54.18
2 Bottom Head 5.0 1 8.87 8.87
3 HH Flange 37 1 40.65 40.65
4 HH Cap & Swing Bolts 37 1 99.07 99.07
6 Hinge Backet 16 1 1.85 1.85
7 Hinge Backet 8 2 0.22 0.45
8 Skirt Support 5 1 13.75 13.75
9 Base Plate 8 1 3.85 3.85
10 Gusset Plate 5 4 0.06 0.25
12 Lifting Lug 16 2 0.96 1.93
13 Nozzle N1 - Neck - 0.15 11.52 1.73 3" SCH 40S
14 Nozzle N1 - Flange - 1 3.70 3.70 3" 150#
15 Nozzle N2 - Neck - 0.15 11.52 1.73 3" SCH 40S
16 Nozzle N2 - Flange - 1 3.70 3.70 3" 150#
17 Nozzle N3 - Neck - 0.46 2.00 0.92 3/4" SCH 80S
18 Nozzle N3 - Flange - 1 0.90 0.90 3/4" 150#
19 Nozzle N4 - Neck - 0.15 2.00 0.30 3/4" SCH 80S
20 Nozzle N4 - Flange - 1 0.90 0.90 3/4" 150#
28 Filter Components - 1 10.00 10.00
Empty Weight 248.7
Weight of Liquid at Operating Level 123.5
Weight of Full Water 139.55
Total Weight of Liquid at Operating Level 372.2
Total Weight of Full Water 388.3
9. Wind load Analysis (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)
Ea
Description Unit Remark
Ea
Ea
Ea
Ea
Ea
Ea
Ea
Ea
Ea
Ea
Ea
m
Ea
m
Ea
m
Ea
m
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 11/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
9.1 Design Data
D : Outside Vessel Diameter = 406 mm
H : Overall Height of Vessel = 1430 mm (Base on GA Drawing)
h ~ H/2 : Distance to the center of the projected area = 715 mm
hT : Distance from base to the skirt to head joint = 288 mm
Exposure Category = B
V : Wind Basic Speed = 39 m/sec = 87.24 mph
G : Gust factor combined with Exposure Coefficient = 0.6
Cf : Shape factor = 0.8
I : Importance factor = 1.08 (As per Specification)
9.2 Design Calculation
Projected area of vessel
Af = D x H = = 580580 mm2
= 0.5806 m2
Velocity pressure
qz = 0.00256 x (IV)2 = 22.727 psf = 1088.2 N/m
2
Design Wind force (Shear force)
F = qz x G x Cf x Af = 303.25 N
Moment at the base plate
M = F x h = 216826 Nmm = 216.83 Nm
Moment at the skirt to head joint
MT = M - hT(F - 0.5 x qz x D x hT) = 147.81 Nm
10. Seismic Analysis (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)
406 x 1430
Page 10 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 12/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
10.1 Design Data
W : Operating Weight of Vessel = 372.2 kg = 3651.5 N
D : Outside Vessel Diameter = 406 mm
H : Overall Height of Vessel = 1430 mm = 4.6916 ft.
X : Distance from top tangent line to the skirt to head joint = 1142 mm (Base on GA Drawing)
Z : Seismic zone factor = 0.4 (Choose Max. Factor)
I : Occupancy Importance coefficient = 1
Rw : Numerical coefficient = 4
Ct : Numerical coefficient = 0.035
S : Site coefficient for soil characteristics = 1.35 (As per Specification)
10.2 Design Calculation
Fundamental period of vibration
T = Ct x H3/4
= 0.112 sec < 0.7 sec
Numberical coefficient
Choose C = 2.75
Total seismic shear
Total horizontal seismic force at top of the vessel
Ft = 0 N ( for T≤ 0.7 sec )
Maximum moment (at the base)
= 957.3 Nm
2.75
= 1004.2=0.4 x 1 x 2.75
4x 3651.5 N
= >7.2812 =1.25×
/3
Page 11 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 13/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
With X = 1142 mm > H/3 = 476.67 mm
Thus
Moment at the skirt to head joint
= 668.1 Nm
11. Skirt Support design for Wind/Seismic (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)
Moment at base in Wind Case
Mw = 216.83 Nm
Moment at the skirt to head joint in Wind Case
MwT = 147.81 Nm
Moment at base in Seismic Case
Ms = 957.3 Nm
Moment at the skirt to head joint in Seismic Case
MsT = 668.1 Nm
Maximum Moment at base in Skirt Support Design
M = = 957.3 Nm
Maximum Moment at the skirt to head joint in Skirt Support Design
MT = = 668.1 Nm
11.1 Design of Skirt thickness
W : Operating Weight of Vessel = 372.22 kg = 3651.5 N
D : Outside Vessel Diameter = 406 mm
R : Outside Vessel Radius = 203 mm
E : Efficiency of skirt to head joint = 0.6 (butt weld as figure above)
S : Allowable Stress value of the head or skirt material = 115 MPa
MT : Maximum Moment at the skirt to head joint = 668.1 Nm
The required skirt thickness
= 0.94 mm
Use 5 mm thickness plate for skirt.
11.2 Design of Anchor Bolt and Base Plate
Max(Mw , Ms)
Max(MwT , MsT)
Head
Skirt
Page 12 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 14/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
W : Operating Weight of Vessel = 372.2 kg = 3651.5 N
D = d : Diameter of anchor bolt circle = 425 mm
dB : Anchor Bolt Size
r : Radius of anchor bolt circle = 212.5 mm
n : Ratio of modulus of elasticity of steel and concrete = 12 (Table E)
f c : Allowable compression strength of concrete = 7.5 MPa (As per Specification)
l1 : Actual Cantilever outside = 45 mm
l2 : Dimension as shown on sketch above = 22.5 mm
l3 : Dimension as shown on sketch above = 27.5 mm
l : Actual Width of Base Plate = 45 mm
S : Allowable stress value of Base plate material = 115 MPa
Sa : Allowable tensile stress in bolts = 138 MPa
M : Maximum Moment at base = 957.3 Nm
Assume 45mm wide Base Ring and a compressive stress at the bolt circle, f cb = 0.8 f c = 6 MPa
Then the constants from Table D are:
Cc = 1.64
Ct = 2.333
j = 0.783
z = 0.427
Required area of anchor bolts
Using 4 anchor bolts, the required root area for one bolt is A = 634.84 / 4 = 158.71 mm2
A ~πdB
2
/4=> d
B= 14.215 mm
Choose Anchor Bolt Size M16 (5/8 in.)
Tensile load on the anchor bolts
Thickness of a ring
=1
1 + 138/(12 x 6)= 0.34
= 7.5 x2 x 0.34 x 425
= 6.50 MPa2 x 0.34 x 425 + 45
= = 634.84 mm22π x
12 x 957.3 - 3651.5 x 0.427 x 425
2.333 x 138 x 0.783 x 425
N=957.3 - 3651.5 x 0.427 x 425
0.783 x 425= 885.42
Page 13 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 15/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
= 0.48 mm
Tensile stress in the anchor bolts
Compressive load on the concrete
= = 4536.9 N
Width of the base ring
= = 44.52 mm
Compressive stress in the concrete at the bolt circle
Checking value of k which was calculated with assumed value of f cb = 6 MPa and Sa = 138 MPa
Then the constant from Table D are:
Cc = 1.884
Ct = 2.113
j = 0.785
z = 0.404
Tensile load on the anchor bolts
Tensile stress in the anchor bolts
Compressive load on the concrete
= = 4641.7 N
Compressive stress in the concrete at the bolt circle
Compressive stress in the anchor bolts
=990.15
0.48 x 212.5 x 2.113= 4.64 MPa
990.15 + 3651.5
= = 0.23 MPa4641.7
(44.52 + 12 x 0.48) x 212.5 x 1.884
=
= 0.259
=885.42
0.48 x 212.5 x 2.333= 3.76 MPa
MPa
=
885.42 + 3651.5
45 - 0.48
=4536.9
(44.52 + 12 x 0.48) x 212.5 x 1.64
=1
1 + 3.76/(12 x 0.259)0.453
957.3 -3651.5 x 0.404 x 425
0.785 x 425= N990.15
Page 14 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 16/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
= = 2.77 MPa
Compressive stress in the concrete at the outer edge of the base ring
Required thickness of base ring (without gussets)
= 3.69 mm
To decrease the thickness of the base ring, use gusset plates.
Using 4 gusset plates, the distance between the gussets,
= 333.79 mm
Ratio
= = 0.1348
Interpolate from table F:
= )2 = 245.8 Nmm
Base ring thickness with gusset
Using thickness of the base plate is 8 mm
12. Lifting Lug Calculation
0.47085 x 0.26 x (45
= 3.58 mm
12 x 0.231
0.26 MPa== 0.23 x2 x 0.453 x 425 + 45
2 x 0.453 x 425
45 / 333.79
Page 15 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 17/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
Equipment weight We = 248.7 kg
Lifting Lug material SA-240M TP304/304L
12.1 Check for β = 90 degrees
Angle β = 90.0 degree
Considered a load factor of 2.0 applied to the structure gravity loads
Design Load P = 2x9.81xWe = 4879.9 N
Force
Fz = 0.5 P = 2440 N
Fx = Fz / tg β = 0 N
Max tensile force in Wire Rope
Ps = Fz / sin β = 2440 N
Lifting lug configuration
where :
SWL = Safe working load
Rh = Hole radius
T = Main plate thickness
h = Base width
b = Distance from edge of taper to center of hole
c = Distance from base of plate to center of hole
D = Shackle pin diameter
Fy = Yield Strength of lifting lug material
The dimension T should equal 60 - 85% of shackle jaw width.
The pin hole diameter should be 3 mm greater than the selected shackle pin size
The main plate radius is approximately R = 3 R h
Choose Shackle
Shackle load Ps = 2440 N = 0.249 tonne
Choose Shackle with SWL = 1.5 tonne
Shackle jaw width W = 19 mm
Shackle pin size D = 13 mm
Page 16 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 18/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. N
Choose Lug Configuration
Rh = 8 mm
a = 18 mm
T = 16 mm
h = 35 mm
b = 50 mm
c = 25 mm
Fy = 170 MPa
Stress in Lifting Lug
Bearing Stress
Bearing = 11.73 MPa Bearing = Ps/(T x D)
Allowable = 153 MPa Allowable = 0.9 x Fy
Safety Factor = 13.04 => PASS
Shear Stress
Shear = 7.62 MPa Shear = Ps/(2(a-Rh)*T)
Allowable = 68 MPa Allowable = 0.4 x Fy
Safety Factor = 8.92 => PASS
Tensile Stress
From Section D3.2 of AISC, the distance used in calculations, across the hole, is the minimum of 4 times
the plate thickness at the pinhole or 0.8 times the hole diameter.
Effective width = 12.8 mm
Plate thickness = 16 mm
Tensile = 11.91 MPa Tensile = Ps/(Effective width*plate thk.) Allowable = 76.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)
Safety Factor = 6.42 => PASS
Bending Stress
Section modulus Z = 3266.7 mm3
Z = h2
x T / 6
Area of lug base A = 560 mm2
A = h x T
Bending = 18.67 MPa Bending = (Fz*c / Z) + (Fx / A)
Allowable = 102 MPa Allowable = 0.6 Fy
Safety Factor = 5.46 => PASS
Stress in Weld Joint
Weld type : T-Butt weld, Full Penetration
Critial weld length K = 16 mm (Assumed equal to the thickness of lug)
Section modulus of weld Zw = 6533 mm Zw = h2
x K / 3
Area of weld Aw = 1120 mm Aw = 2 x K x h
Applied by force Fz
Bending S1 = 9.3 MPa Bending S1 = Fz*c/Zw
Shear S2 = 2.2 MPa Shear S2 = Fz/Aw
Page 17 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 19/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
Combined = 9.59 MPa Combined = (S12
+ S22)0.5
Allowable = 102 MPa Allowable = 0.6 Fy
Safety Factor = 10.64 => PASS
Applied by force Fx
Tensile S3 = 0.00 MPa Tensile S3 = Fx/Aw
Allowable = 102 MPa Allowable = 0.6 Fy
=> PASS
12.2 Check for β = 85 degrees (Considering Tolerance 5 degrees)
Angle β = 85.0 degree
Considered a load factor of 2.0 applied to the structure gravity loads
Design Load P = 2x9.81xWe = 4879.9 N
Force
Fz = 0.5 P = 2440 N
Fx = Fz / tg β = 213 N
Max tensile force in Wire Rope
Ps = Fz / sin β = 2449 N
Choose Shackle
Shackle load Ps = 2449 N = 0.250 tonne
Choose Shackle with SWL = 1.5 tonne
Stress in Lifting Lug
Bearing Stress
Bearing = 11.78 MPa Bearing = Ps/(T x D)
Allowable = 153 MPa Allowable = 0.9 x Fy
Safety Factor = 12.99 => PASS
Shear Stress
Shear = 7.65 MPa Shear = Ps/(2(a-Rh)*T)
Allowable = 68 MPa Allowable = 0.4 x Fy
Safety Factor = 8.88 => PASS
Tensile Stress
From Section D3.2 of AISC, the distance used in calculations, across the hole, is the minimum of 4 times
the plate thickness at the pinhole or 0.8 times the hole diameter.
Effective width = 12.8 mm
Plate thickness = 16 mm
Tensile = 11.96 MPa Tensile = Ps/(Effective width*plate thk.)
Allowable = 76.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)
Safety Factor = 6.40 => PASS
Bending Stress
Section modulus Z = 3266.7 mm3
Z = h2
x T / 6
Area of lug base A = 560 mm2
A = h x T
Bending = 19.05 MPa Bending = (Fz*c / Z) + (Fx / A)
Allowable = 102 MPa Allowable = 0.6 Fy
Page 18 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 20/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. N
Safety Factor = 5.35 => PASS
Stress in Weld Joint
Weld type : T-Butt weld, Full Penetration
Critial weld length K = 16 mm (Assumed equal to the thickness of lug)
Section modulus of weld Zw = 6533 mm Zw = h2
x K / 3
Area of weld Aw = 1120 mm Aw = 2 x K x h
Applied by force Fz
Bending S1 = 9.3 MPa Bending S1 = Fz*c/Zw
Shear S2 = 2.2 MPa Shear S2 = Fz/Aw
Combined = 9.59 MPa Combined = (S12
+ S22)0.5
Allowable = 102 MPa Allowable = 0.6 Fy
Safety Factor = 10.64 => PASS
Applied by force Fx
Tensile S3 = 0.19 MPa Tensile S3 = Fx/Aw
Allowable = 102 MPa Allowable = 0.6 Fy
Safety Factor = 535.16 => PASS
Choose Lug Configuration as shown above is satisfactory
13. Hydrotest Pressure (Refer to ASME Section VIII, Division 1, UG-99 (b))
Design Temperature = 105 degrees C
Test Temperature = A.T.M
Internal Design Pressure P = 1.18 MPa
Max. Allowable Stress at Design Temperature Sd = 115 MPa
Max. Allowable Stress at Test Temperature St = 115 MPa
Hydrotest Pressure Ph = 1.3 x P x (St/Sd)
Ph = 1.3 x 1.18 (115/115) = 1.534 MPa
14. Conclusion
Shell thickness:
Thickness required: 2.50 mm
Thickness actual: 5 mm
Bottom Head thickness:
Min. Thickness required: 2.03 mm
Top Head thickness:
Min. Thickness required: 37.00 mm
Swing bolt diameter : 16 mm
Nozzle thickness:
Nozzle Neck N1, N2_DN 80 (3")
Thickness required: 2.50 mm
Thickness actual: 5.49 mm
Nozzle Neck N3_DN 20 (3/4")
Page 19 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 21/25
Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No
Thickness required: 2.50 mm
Thickness actual: 3.91 mm
Nozzle Neck N4_DN 20 (3/4")
Thickness required: 2.51 mm
Thickness actual: 3.91 mm
MDMT for all items of equipment:
MDMT = 6 degree C
Nozzle reinforcement:
Nozzle Neck N1, N2_DN 80 (3")
Material SA-240 TP304/304L
Outside diameter = 150 mm
Thickness = 5 mm
Skirt thickness:
Thickness required: 0.94 mm
Thickness actual: 5 mm
Anchor Bolt:
Anchor Bolt Size: M16 (5/8 in.)
Base Plate:
Thickness required: 3.58 mm
Thickness actual: 8 mm
Hydrotest Pressure: 1.534 MPa = 15.34 bar
Page 20 o
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 22/25
ASME B16.5
SA-240 TP304
SA-312 TP304
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 23/25
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 24/25
7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)
http://slidepdf.com/reader/full/v-2151-102-a-216-c-design-calculation-sheet-filter 25/25